US10670149B2 - Gas seal - Google Patents

Gas seal Download PDF

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Publication number
US10670149B2
US10670149B2 US16/330,879 US201716330879A US10670149B2 US 10670149 B2 US10670149 B2 US 10670149B2 US 201716330879 A US201716330879 A US 201716330879A US 10670149 B2 US10670149 B2 US 10670149B2
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Prior art keywords
slide
seal
gas seal
pressure element
stationary
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US16/330,879
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US20190186635A1 (en
Inventor
Christian Kirchner
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Siemens Energy Global GmbH and Co KG
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Siemens AG
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Assigned to SIEMENS AKTIENGESELLSCHAFT reassignment SIEMENS AKTIENGESELLSCHAFT ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KIRCHNER, CHRISTIAN
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/3464—Mounting of the seal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/36—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member connected by a diaphragm or bellow to the other member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/38—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member sealed by a packing

Definitions

  • the invention relates to a gas seal, in particular dry gas seal, which extends in a circumferential direction with respect to an axis, comprising a rotating slide ring and a stationary slide ring, wherein the stationary slide ring is axially movable, wherein the gas seal comprises a slide sleeve, wherein, the gas seal comprises a pressure element which bears against the stationary slide ring at a first contact surface by means of a second contact surface, wherein, by means of the pressure element, an elastic element axially presses the stationary slide ring by way of the sealing surface of the latter against the rotating slide ring RSR.
  • a gas seal in particular dry gas seal, which extends in a circumferential direction with respect to an axis, comprising a rotating slide ring and a stationary slide ring, wherein the stationary slide ring is axially movable, wherein the gas seal comprises a slide sleeve, wherein, the gas seal comprises a pressure element which bears against the stationary slide ring at
  • Dry gas seals of said type generally comprise components composed of ceramic, in particular manufactured from silicon carbide or tungsten carbide.
  • the ceramic components are normally the stationary and/or rotating slide rings and, if appropriate, adjoining elements.
  • a further example from the patent literature is given by DE 39 25 403 C2.
  • both the rotating sealing ring and the stationary sealing ring are sealed off with respect to the rotor or stator (housing and possibly connected components) by means of a substantially static seal. Owing to the possible axial vibrations, it is necessary for at least one of these seals to be axially movable. This is generally at least the stationary seal because the mobility is easier to realize at this component. Owing to the high dynamics of the movements, this secondary seal is subjected to extreme loading.
  • seal SSL Secondary seal
  • the gas seal according to the invention is designed in the form of a shaft seal.
  • the shaft seal or the gas seal according to the invention is designed in the form of an independently transportable insert (often also referred to as a cartridge), with the result that this modularity allows for example simple replacement of a defective gas seal with an intact gas seal.
  • the stator it is also possible for the stator to be a direct, if appropriate single-piece, component of the housing of the machine in which the gas seal is installed, for example a radial turbocompressor.
  • seal is designed so as to consist at least partially of Teflon.
  • the pressure element has two circumferentially extending portions which are able to be separated from one another, a first portion, against which the elastic element bears, and a second portion, which has the second contact surface, wherein the seal is arranged at least partially with a fastening portion between the two portions.
  • One advantageous refinement of the invention provides that the second portion comprises the third slide surface.
  • One advantageous refinement of the invention provides that the first portion consists substantially of metal.
  • One advantageous refinement of the invention provides that the second portion consists substantially of ceramic.
  • the guide sleeve consists of ceramic, in particular of silicon carbide or tungsten carbide.
  • the slide ring and the slide sleeve advantageously consist of said ceramics owing to their permanently high dimensional accuracy requirements.
  • seal extends radially inward beyond the contact surface between the two portions of the pressure element, and also extends axially beyond the transition point between the pressure element and the slide sleeve on an axial side with the higher pressure.
  • One advantageous refinement of the invention provides that, by means of the first slide surface, the slide sleeve radially guides the stationary slide ring on a second slide surface along the axial direction of mobility.
  • One advantageous refinement of the invention provides that, with respect to the first slide surface, the third slide surface has smaller radial play than the second slide surface.
  • one advantageous refinement proposes that the slide sleeve is fastened to a stator of the gas seal, wherein the slide sleeve has a first recess, extending in the circumferential direction, and the stator has a second recess, extending in the circumferential direction and situated opposite the first recess in the region of the fastening, such that the first recess and the second recess define a common cavity, which extends in the circumferential direction in an annular manner, wherein, in the cavity, there is arranged an elongate fixing element which at least partially fills the first recess and second recess such that an unlimited axial relative movement is possible only when the fixing element is radially deformed.
  • slide sleeve consists of ceramic and the stator consists of metal.
  • stator or the slide sleeve has an insertion channel, opening out into the cavity, such that the fixing element is able to be introduced into the cavity through the insertion channel.
  • Another advantageous refinement provides that the insertion channel runs, at least in portions, substantially tangentially with respect to the cavity.
  • slide sleeve and/or the stationary slide ring and/or the second portion consist/consists, at least in portions or completely, of tungsten carbide or silicon carbide.
  • the fixing element is designed in the form of a helical spring, in particular in the form of a tube spring or worm spring.
  • the fixing element is also designed in a manner deformable in the radial direction.
  • the fixing element may be designed in particular in the form of a helical spring and particularly advantageously in the form of a tube spring or worm spring.
  • the fixing element it is possible here for the fixing element to consist of an elastic material or for example of a helically shaped steel profile which particularly advantageously has a flat profile.
  • the helical spring or the fixing element can be introduced into the cavity in a manner substantially free of play or can be arranged in the cavity such that the slide sleeve is securely fastened to the stator.
  • An elastic deformation of the fixing element gives rise to the additional advantage of an elasticity of the gas seal, in particular in the axial direction.
  • the fixing according to the invention of the slide sleeve is sufficient for establishing the required stability, in particular with respect to vibrations. Since the rotor also vibrates axially in the case of for example a turbomachine, the additional axial elasticity in the fastening of the slide sleeve is particularly advantageous for the seal.
  • FIG. 1 shows a schematic longitudinal section through a gas seal according to the invention.
  • FIG. 1 shows a schematic longitudinal section through a gas seal according to the invention with an adjoining housing CAS and an adjoining shaft SH.
  • the gas seal DGS according to the invention is designed in the form of an insert which is able to be transported independently of the housing CAS and the shaft SH.
  • a rotor ring RRG is fastened radially and axially on the shaft SH by means of two shoulders SH 1 , SH 2 , wherein the two shoulders SH 1 , SH 2 , are fastened in a detachable manner to the shaft SH in a way not illustrated in more detail.
  • the rotor ring RRG has, toward the shaft SH, a rotating static seal RSS.
  • a rotating slide ring RSR is fastened to the rotor ring RRG by means of a worm spring RSE, wherein the worm spring RSE allows an axial movement of the rotating slide ring RSR out of the target position only with radial deformation.
  • the rotating slide ring RSR is sealed off with respect to the rotor ring RRG by way of a second rotating seal RS 2 .
  • Axially opposite a sealing surface CSF 1 of the rotating slide ring RSR is a stationary slide ring SSR with a corresponding sealing surface CSF 2 , wherein, by means of a pressure element PSE, a spring SPR axially presses the stationary slide ring SSR by way of the sealing surface CSF 2 of the latter against the rotating slide ring RSR.
  • the pressure element PSE is split axially into two portions which extend in a circumferential direction, a first portion PSE 1 and a second portion PSE 2 , wherein, by means of the spring SPR, the two portions are pressed axially against one another and axially against the stationary slide ring SSR.
  • the first portion PSE 1 is of metallic design
  • the second portion PSE 2 is of ceramic design, advantageously being composed of the same ceramic as a slide sleeve SLV which extends in a circumferential direction and which serves as a guide for an axial movement of the pressure element PSE and the stationary slide ring SSR.
  • the play between the slide sleeve SLV and the second portion PSE 2 is formed to be small, with the result that the second portion, and thus the entire pressure element PSE, is guided in a manner radially mounted and axially displaceable.
  • One advantageous refinement of the invention provides that a first slide surface SSF 1 of the slide sleeve SLV radially guides a second slide surface SSF 2 of the stationary slide ring SSR on along the axial direction of mobility.
  • the first slide surface SSF 1 of the slide sleeve SLV also guides a third slide surface SSF 3 of the second portion PSE 2 along the axial direction of mobility.
  • the radial play between the slide sleeve SLV and the second portion PSE 2 advantageously amounts to less than 1 mm with respect to the diameter, with the result that the second portion, and thus the entire pressure element PSE, is guided in a manner radially mounted and axially displaceable.
  • the second portion PSE 2 bears with an axial projection APR, which has a first axial contact surface CS 1 , against a second contact surface CS 2 of the stationary slide ring SSR.
  • the two contact surfaces CS 1 , CS 2 are formed in a manner lapped against one another, with the result that the almost play-free contact acts as a seal.
  • a circumferentially extending seal SSL which is designed in the form of a Teflon seal TFL, is arranged and held on the stationary slide ring SSR by means of the contact pressure of the pressure element PSE 1 such that the two first portions PSE 1 , PSE 2 bear sealingly against one another.
  • the stationary slide ring SSR is guided in a manner axially displaceable on the slide sleeve SLV with little radial play such that the mobility degree of freedom is limited to the axial movement.
  • the second portion PSE 2 of the pressure element PSE is likewise mounted. Both the stationary slide ring SSR and the slide sleeve SLV and also the second portion PSE 2 are manufactured from tungsten carbide or silicon carbide.
  • the seal SSL of the pressure element PSE extends radially inward beyond the contact surface between the two portions PSE 1 , PSE 2 of the pressure element PSE.
  • the seal SSL also extends axially beyond the transition point between the pressure element PSE and the slide sleeve SLV on the side with the higher pressure. Owing to the small radial play between the slide sleeve SLV and the second portion PSE 2 of the pressure element PSE (which is also smaller than the play between the stationary slide ring SSR and the slide sleeve SLV), the seal SSL is, under pressure, extruded only slightly into this radial gap such that sealing is ensured.
  • the stationary slide sleeve SLV is fastened to a stator STS by means of a fastening element FXE, wherein the stator STS is at the same time a housing CSC of the gas seal DGS.
  • a cavity CAV is defined by a first recess RZ 1 , extending in a circumferential direction CDR, of the slide sleeve SLV and by a second recess RZ 2 , extending in the circumferential direction CDR and situated opposite in the region of the fastening, of the stator STS.
  • the housing CSC of the gas seal DGS is sealed off with respect to the housing CAS of the turbomachine by means of an O-ring seal ORG.
  • the housing of the turbomachine and the housing CSC of the gas seal DGS to be a single component.
  • the fixing element FXE is able to be introduced tangentially into the cavity CAV through a substantially tangential insertion channel ASC.
  • the fixing element FXE is designed in the form of a worm spring and, accordingly, it is basically a helical spring, advantageously composed of a metallic material.
  • a stator seal SSS is also provided between the slide sleeve SLV and the stator STS to maintain the pressure difference between the outer pressure P 1 and the inner pressure P 2 .
  • the seal SSL or Teflon seal TFL is, by means of a helical spring element HSC extending in the circumferential direction CDR, pressed radially with the radially inner, projecting end against the slide sleeve SLV such that any differential pressure, in particular in the region between the static slide ring SSR and the slide sleeve SLV, in this case between the pressure element PSE and the slide sleeve SLV, is sealed off by the Teflon seal TFL.
  • the Teflon seal TFL is partially extruded into a gap between the slide sleeve SLV and the pressure element.
  • the helical spring element HSC holds the Teflon seal TFL merely in the position suitable for this purpose.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Sealing (AREA)
US16/330,879 2016-09-13 2017-08-14 Gas seal Active US10670149B2 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
EP16188481 2016-09-13
EP16188481.2 2016-09-13
EP16188481.2A EP3293426A1 (de) 2016-09-13 2016-09-13 Gasdichtung
PCT/EP2017/070543 WO2018050378A1 (de) 2016-09-13 2017-08-14 Gasdichtung

Publications (2)

Publication Number Publication Date
US20190186635A1 US20190186635A1 (en) 2019-06-20
US10670149B2 true US10670149B2 (en) 2020-06-02

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ID=56920613

Family Applications (1)

Application Number Title Priority Date Filing Date
US16/330,879 Active US10670149B2 (en) 2016-09-13 2017-08-14 Gas seal

Country Status (5)

Country Link
US (1) US10670149B2 (de)
EP (2) EP3293426A1 (de)
CN (1) CN109715994B (de)
RU (1) RU2697019C1 (de)
WO (1) WO2018050378A1 (de)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020113068A1 (de) * 2020-05-14 2021-11-18 Eagleburgmann Germany Gmbh & Co. Kg Gleitringdichtungsanordnung für Hochtemperaturanwendungen

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3925403A1 (de) 1989-07-12 1991-01-24 Escher Wyss Gmbh Trockengasdichtung
US5370403A (en) * 1992-12-16 1994-12-06 Durametallic Corporation Non-contacting face seal
WO1996004497A1 (en) 1994-08-05 1996-02-15 Durametallic Corporation Mechanical seal with spring drive
DE20217983U1 (de) 2002-11-20 2003-02-13 Burgmann Dichtungswerke Gmbh Sekundärdichtungselement
DE202007012050U1 (de) 2007-08-29 2007-10-25 Burgmann Industries Gmbh & Co. Kg Dichtungselement, insbesondere Sekundärdichtungselement einer Gleitringdichtung
DE102011007071A1 (de) 2011-04-08 2012-10-11 Siemens Aktiengesellschaft Wellendichtungseinsatz
US8523186B2 (en) * 2005-07-14 2013-09-03 Eagleburgmann Germany Gmbh & Co. Kg Slide ring seal arrangement
WO2014023581A1 (de) 2012-08-10 2014-02-13 Siemens Aktiengesellschaft Wellendichtungsanordnung
WO2014037150A1 (de) 2012-09-07 2014-03-13 Siemens Aktiengesellschaft Anordnung mit einer gasdichtung

Patent Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3925403A1 (de) 1989-07-12 1991-01-24 Escher Wyss Gmbh Trockengasdichtung
US5370403A (en) * 1992-12-16 1994-12-06 Durametallic Corporation Non-contacting face seal
WO1996004497A1 (en) 1994-08-05 1996-02-15 Durametallic Corporation Mechanical seal with spring drive
US5558342A (en) * 1994-08-05 1996-09-24 Durametallic Corporation Mechanical seal with spring drive
DE20217983U1 (de) 2002-11-20 2003-02-13 Burgmann Dichtungswerke Gmbh Sekundärdichtungselement
US7240904B2 (en) 2002-11-20 2007-07-10 Burgmann Industries Gmbh & Co. Kg Secondary sealing element
US8523186B2 (en) * 2005-07-14 2013-09-03 Eagleburgmann Germany Gmbh & Co. Kg Slide ring seal arrangement
WO2009030298A1 (de) 2007-08-29 2009-03-12 Burgmann Industries Gmbh & Co. Kg Dichtungselement, insbesondere sekundärdichtungselement einer gleitringdichtung
DE202007012050U1 (de) 2007-08-29 2007-10-25 Burgmann Industries Gmbh & Co. Kg Dichtungselement, insbesondere Sekundärdichtungselement einer Gleitringdichtung
DE102011007071A1 (de) 2011-04-08 2012-10-11 Siemens Aktiengesellschaft Wellendichtungseinsatz
US9518473B2 (en) 2011-04-08 2016-12-13 Siemens Aktiengesellschaft Shaft seal insert
WO2014023581A1 (de) 2012-08-10 2014-02-13 Siemens Aktiengesellschaft Wellendichtungsanordnung
WO2014037150A1 (de) 2012-09-07 2014-03-13 Siemens Aktiengesellschaft Anordnung mit einer gasdichtung
US20150240951A1 (en) 2012-09-07 2015-08-27 Siemens Aktiengesellschaft Arrangement with a gas seal
RU2622445C2 (ru) 2012-09-07 2017-06-15 Сименс Акциенгезелльшафт Система с газовым уплотнением

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
International search report and written opinion dated Nov. 21, 2017, for corresponding PCT/EP2017/070543.

Also Published As

Publication number Publication date
EP3485185A1 (de) 2019-05-22
US20190186635A1 (en) 2019-06-20
CN109715994B (zh) 2023-03-10
WO2018050378A1 (de) 2018-03-22
CN109715994A (zh) 2019-05-03
EP3293426A1 (de) 2018-03-14
RU2697019C1 (ru) 2019-08-08
EP3485185B1 (de) 2020-09-30

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